EP0389643A1

EP0389643A1 - Direct-acting impact ripper

Info

Publication number: EP0389643A1
Application number: EP89910932A
Authority: EP
Inventors: Norihisa Matsumoto; Masao Murakami
Original assignee: Komatsu Ltd
Current assignee: Komatsu Ltd
Priority date: 1988-09-30
Filing date: 1989-09-28
Publication date: 1990-10-03
Also published as: US5094017A; WO1990003473A1; JPH0278647U; JPH072736Y2; EP0389643A4

Abstract

The apparatus according to the present invention is a direct-acting impact ripper for transmitting a striking force of a hydraulic breaker to a rock efficiently. This impact ripper has a bracket (2) fixed to the rear portion of a chassis of a construction machine. At the rear side of the bracket (2), various parts are provided, which include a beam (4) to which a breaker mounting bracket (9) having a shank (8) and a hydraulic breaker (10) is fixed, an arm (6) connecting the lower portions of the bracket (2) and beam (4) together, a tilting cylinder (5) connecting the upper portions of the bracket (2) and beam (4) together, and a lift cylinder (16) connecting the upper portion of the bracket (2) and the lower portion of the beam (4) together. The beam (4) and shank (8) are provided with a pair of link members (7), which support the beam (4) and shank (8) pivotably so that these parts form a quadric link. Since the shank (8) is moved linearly owing to the quadric link to transmit a force to a rock efficiently, a ripping limit with respect to a hard rock is heightened, and a ripping workload increases.

Description

Technical Field

The present invention relates to a parallel linkage type shock ripper device, and more particularly, to a direct driven shock ripper device which enables blows of a hydraulic breaker to be efficiently transferred to a base rock.

Background Art

Conventionally, when base rocks are to be dug (ripping operation) by a construction machine such as a bulldozer, a parallel link type shock ripper device 1 is mounted on a rear 2 of the vehicle, as shown in Fig. 6. A shank 8 is forced into the base rock by the depressing force generated by the weight of the bulldozer. The base rock is broken up by utilizing the towing force of the bulldozer and the hydraulic force of a tilt cylinder 5. The ability with which the bulldozer breaks up the base rock is substantially proportional to the weight of the vehicle. Thus, the hardness of the base rocks at the operation site is investigated beforehand, and a vehicle which suits the operation condition is selected.
When hard rocks that cannot be broken up by such an operation exist, they are cracked by utilizing the blows of a hydraulic breaker 10 mounted on the ripper device 1 to facilitate breaking (as is disclosed in Japanese Utility Model Laid-Open No. 35068/1987). The blows F given by the hydraulic breaker 10 are transferred from a blowing surface 8b of the shank 8 to the base rock through a ripper point 17 provided at one end of the shank 8, as shown in Fig. 7. However, since a shank rotating shaft 8a provided at the other end of the shank 8 is pivotally supported on an arm 6, the ripper point 17 revolves in the form of an arc around the shank rotating shaft 8a. In consequence, the blow F exerted on the base rock is reduced, and the function of the hydraulic breaker 10 cannot be fully utilized. As a result, the base rock cannot be broken regularly, and this makes the vehicle jolt much when it travels in reverse, providing uncomfortable ride. Furthermore, since the ripper point 17 cannot be forced into the rock much, the ripper point 17 slips often, increasing wear of the ripper point. Also, caterpillars slip often, increasing wear or damage thereof. In view of the aforementioned problem, an object of the present invention is to provide a direct driven shock ripper device which is capable of efficiently transferring blows of a hydraulic breaker to a base rock.

Disclosure of Invention

To this end, the present invention provides a direct driven type shock ripper device which includes a bracket fixed to a rear of a vehicle which is a construction machine, a beam on which a shank and a hydraulic breaker which givens impacts to the shank are mounted, the beam being disposed at the back of the bracket, an arm which interconnects a lower portion of the bracket to a lower portion of the beam, a tilt cylinder which interconnects an upper portion of the bracket to an upper portion of the beam, the bracket, the beam, the arm and the tilt cylinder in combination form a parallel linkage, and a lift cylinder provided between the upper portion of the bracket and the lower portion of the beam. The shank is mounted on the beam through a pair of link members to form a quadric linkage. In consequence, blows of the hydraulic breaker can be efficiently transferred to a base rock in the form of a linear motion of the shank. This facilitates breaking or cracking of the base rock and improves the ripping operability.

Brief Description of Drawings

Fig. 1 is a side elevational view of an embodiment of a direct operated shock ripper device according to the present invention;
Fig. 2 is a cross-sectional view showing a state in which a ripper shank is mounted on a beam;
Fig. 3 is a section taken along the line A - A of Fig. 1;
Fig. 4 is a section taken along the line B - B of Fig. 1;
Figs. 5 (a) and 5 (b) are respectively sections taken along the lines C - C and D - D of Fig. 1;
Fig. 6 is a side view of a bulldozer with a conventional shock ripper device; and
Fig. 7 illustrates the conventional shock ripper device.

Best Mode for Carrying Out the Invention

Fig. 1 is a side elevational view of an embodiment of a direct driven shock ripper device according to the present invention. This direct driven shock ripper device includes a bracket 3 fixed to a rear 2 of a vehicle, and a beam 4 disposed at the rear of the bracket 3, an arm 6 which couples the lower portion of the bracket 3 and the lower portion of the beam 4, a tilt cylinder 5 which interconnects the upper portion of the bracket 3 to the upper portion of the beam 4, and a lift cylinder 6 extending between the upper portion of the bracket 3 and the lower portion of the beam 4. A shank 8 is mounted on the beam 4, and a hydraulic breaker 10 is incorporated in the beam 4. The shank 8 is pivotally supported on the beam 4 through a pair of link members 7. A ripper point 17 is mounted on the forward end of the shank 8. The hydraulic breaker 10 is held above a blowing surface provided on the rear end of the shank 8 by a breaker mount bracket 9 mounted on the beam 4.
Fig. 2 is a cross-sectional view showing a state in which the shank 8 is pivotally supported on the beam 4 by means of the pair of link members 7. Each of the links 7 is pivotally supported on the beam 4 at one end thereof P or Q. The other ends S and T of the links 7 are supported on the shank 8. The 4 points, P, Q, S and T form a quadric linkage which moves the shank 8 in a straight line when the hydraulic breaker 10 strikes the shank 8. Link member stoppers 4a and 4b are mounted on the beam 4 to limit the linear motion of the shank 8 which occurs when loads are applied to the shank 8.
Fig. 3 is a section taken along the line A - A of Fig. 1. The one end P of the link 7 is pivotally supported on the beam 4 through an elastic bushing 11, and the other end S is pivotally supported on the shank 8
Fig. 4 is a section taken along the line B - B of Fig. 1. The one end Q of the link 7 is pivotally supported on the beam 4 through the elastic bushing 11, and the other end T is pivotally supported on the shank 8. The breaker mount bracket 9 is pivotally supported on the beam 4 through an elastic bushing 12.
Figs. 5 (a) and (b) are respectively sections taken along the lines C - C and D - D of Fig. 1. An upper side stopper 13 and a lower side stopper 14 are mounted on the inner side of the beam 4 in such a manner that they grip the shank 8 to receive the lateral deflection generated in the shank 8 when the vehicle is swivelled. An elastic bushing 15 is mounted on the inner side of the breaker mount bracket 9 to prevent lateral deflection generated in the hydraulic breaker 10 when it strikes the shank 8.
When the bulldozer with the thus-arranged direct driven shock ripper device is operated for a normal ripping operation, the lift cylinder 16 is stretched, as shown in Fig. 1. Thereafter, the shank 8 is forced into the ground by the depressing force caused by the weight of the vehicle, and the base rock is broken up by utilizing the pulling force of the vehicle and the pulling up force of the tilt cylinder 5. The pulling force, depressing force and pulling up force are received by the pair of link member stoppers 4a and 4b mounted on the beam 4. The lateral force generated when the vehicle is swivelled is received by the upper and lower side stoppers 13 and 14 mounted on the inner side of the beam 4. When there exists a base rock that cannot be broken by the normal ripping operation, a blow is given to the blowing surface 8a of the shank 8 by the hydraulic breaker 10. At that time, since the shank 8 is pivotally supported on the beam 4 by means of the pair of link members 7, as shown in Fig. 2, the shank 8 moves in a straight line (in directions indicated by the arrows), allowing the blowing force to be efficiently transferred to the base rock through the ripper point 17 mounted on the forward end of the shank 8. Thus, the hard rock ripping limit (elastic wave speed) increases, and ripping operability therefore increases. The vibrations generated in the hydraulic breaker 10 and the shank 8 at this time are alleviated by the elastic bushings 12 and 11 respectively mounted on the breaker mount bracket 9 and the links 7. The transverse deflection caused by the vibrations of the hydraulic breaker 10 are absorbed by the transverse deflection preventing elastic bushing 15 mounted on the breaker mount bracket 9.

Industrial Applicability

As will be understood from the foregoing description, in the direct driven shock ripper device according to the present invention, it is possible to improve the ripping limit of a hard rock and thus increase the ripping operability. It is also possible to provide a comfortable ride and prolong the life of the ripper point or caterpillars.

Claims

1. A direct driven type shock ripper device including a bracket fixed to a rear of a vehicle which is a construction machine, a beam on which a shank and a breaker mount bracket supporting a hydraulic breaker are mounted, said beam being disposed at the rear of said bracket, an arm which couples a lower portion of said bracket to a lower portion of said beam, a tilt cylinder which couples an upper portion of said bracket to an upper portion of said beam, and a lift cylinder which couples the upper portion of said bracket to the lower portion of said beam,
an improvement being characterized in that a pair of link members are provided to pivotally support said shank and said beam and thereby form a quadric linkage.

2. A direct driven type shock ripper device according to claim 1, wherein said beam is provided with a pair of link member stoppers which limit the linear motion of said shank caused by said link members, and wherein an elastic bushing for absorbing vibrations of said shank is provided at portions of the beam at which said link members are pivotally supported.

3. A direct driven type shock ripper device according to claim 1, wherein said beam is provided with a pair of upper and lower side stoppers which grip said shank and thereby receive a lateral force generated in said shank when the vehicle is swivelled.

4. A direct driven type shock ripper device according to claim 1, wherein an elastic bushing for absorbing vibrations of said hydraulic breaker is provided at a portion of said beam at which said breaker mount bracket is mounted, and wherein said breaker mount bracket is provided with an elastic bushing which prevents lateral deflection of said hydraulic breaker when it gives a blow.